EP2464872B1 - Pompe à palettes équilibrée en pression, à déplacement variable, à deux lobes et une bague - Google Patents

Pompe à palettes équilibrée en pression, à déplacement variable, à deux lobes et une bague Download PDF

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Publication number
EP2464872B1
EP2464872B1 EP10808606.7A EP10808606A EP2464872B1 EP 2464872 B1 EP2464872 B1 EP 2464872B1 EP 10808606 A EP10808606 A EP 10808606A EP 2464872 B1 EP2464872 B1 EP 2464872B1
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EP
European Patent Office
Prior art keywords
cam ring
rotor
pump
vanes
pressure plate
Prior art date
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Active
Application number
EP10808606.7A
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German (de)
English (en)
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EP2464872A4 (fr
EP2464872A2 (fr
Inventor
Alexander J. Kurylowski
Anita I. Jacobs
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Woodward Inc
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Woodward Inc
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Publication of EP2464872A4 publication Critical patent/EP2464872A4/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F02M37/04—Feeding by means of driven pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/10—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • F04C15/0049—Equalization of pressure pulses
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3446—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along more than one line or surface

Definitions

  • This invention relates to pumps generally, and more particularly to variable displacement vane pumps.
  • Positive displacement pumps specifically vane-type positive displacement pumps
  • these vane pumps include a slotted rotor configured to accept closely fitted but free moving vanes.
  • the rotor may be splined to accept a splined pump drive shaft.
  • a lobe shaped cam ring surrounding the rotor defines at least one pumping chamber.
  • Pressure plates may be positioned on either side of the cam ring/rotor assembly.
  • the pressure plates include flow passages (i.e., inlets and outlets) for fluid entering and leaving the pumping chamber.
  • the pumping cycle is started when the rotor turns as the drive shaft is rotated.
  • the centrifugal force acting on the vanes causes them to slide outward, or extend, in the rotor vane slots until they contact the contoured cam ring.
  • the vanes "track” against the contour of the cam ring.
  • the intake cycle when fluid is drawn into the pumping chamber, the clearance between the rotor and the cam ring increases and fluid is taken in to fill the spaces between the vanes left by the rising cam. This is also known as the intake cycle.
  • the cam blends into the major diameter.
  • the vanes after passing through the major dwell portion of the cam, begin to retract on the descending cam contour.
  • fluid is forced out of the spaces between the vanes by the falling cam contour. This is also known as the discharge cycle.
  • dual-lobe cam ring vane pumps can be varied by rotating the cam ring.
  • one problem associated with dual-lobe variable displacement pumps is pressure pulsation in the transition region. This may occur in the transition from thus producing a rapid increase in pressure.
  • Another problem with dual-lobe variable displacement pumps is cavitation in the transition region from discharge to inlet. This may occur when there is insufficient fill area relative to the volume expansion rate, thus producing a rapid decrease in pressure. Both of these problems expose the pump components to severe mechanical stresses which can reduce the reliability and the lifetime of the pump.
  • variable displacement pump with a dual-lobe cam ring, that reduces or eliminates cavitation and pressure pulsation during pump operation.
  • Embodiments of the invention reduce or eliminate the aforementioned cavitation and pressure pulsation.
  • US 2007/0134120 A1 describes a vane pump in which a position of a first suction port located in the forward rotation direction of a rotor is brought closer to a suction port than a position of a second suction port located in the backward rotation direction of the rotor with the suction port as reference by positioning a side plate in the state where the discharge port is brought close to a mounting portion.
  • the cam In a standard dual lobe vane pump in the inlet and discharge transitions the cam has a very low gain (Dvol/Ddeg), and the high gain portion of the cam occurs when the ports have a relatively large area. Inherent to the variable concept, when the cam is rotated the high gain portion of the cam now occurs in the transition region when the port openings are very small. A second set of ports have been added to increase the available area to either port the flow in (as required in the discharge to inlet zone) or port the flow out (as required in the inlet to discharge zone).
  • FIG. 1 illustrates an exploded view of a balanced pressure, variable displacement, dual lobe, single ring vane pump 100 according to an embodiment of the invention.
  • the vane pump 100 includes the rotor 102 having a plurality of radial slots, wherein the rotor 102 is disposed within a cam ring 104.
  • the rotor 102 and cam ring 104 are sandwiched between two pressure plates 106, 108, and are axially and radially positioned within a central opening of a spacer 110.
  • the rotor 102 is configured to be driven by a splined drive shaft (not shown), which may be attached to a motor (not shown). Pins may be used to align the pressure plates 106, 108 with the spacer 110.
  • FIG. 2 illustrates the rotor 102 according to an embodiment of the invention.
  • the rotor 102 has ten radial slots 112, each configured to house a vane 114. However, in alternate embodiments of the invention, the rotor 102 may have more or less than ten slots 112. In the embodiment shown, the radial slots are uniformly spaced around the circumference of the rotor 102. At its center, the rotor 102 further includes a circular opening which may be splined to accept the drive shaft (not shown). Between each pair of adjacent slots 112 is a cut out or notch 118. The slots 112 and vanes 114 are configured such that the vanes 114 are close-fitting, but free to extend and retract radially within the slots 112.
  • FIG. 3 illustrates the cam ring 104 according to an embodiment of the invention.
  • the cam ring 104 has a circular outer diameter 120, and a dual-lobed inner diameter 122.
  • the inner diameter 122 includes lobed portions 124, 126 and non-lobed portions 128, 130.
  • the lobed portions 124, 126 define a major diameter 125, while the non-lobed portions 128, 130 define a minor diameter 129, wherein the major diameter 125 is larger than the minor diameter 129.
  • the cam ring 104 has handle-like projections 132 for rotating the cam ring 104 while the pump is operating, so that pump displacement can be dynamically adjusted during pump operation.
  • the C-shaped spacer 110 (shown in FIG.
  • the cam ring 104 has an inner diameter 122 that is a lobed circle, wherein the inner diameter 122 includes two opposing lobes spaced 180 degrees apart from each other on the inner diameter 122.
  • FIG. 4 is an illustration of the pressure plate 106 according to an embodiment of the invention.
  • the pressure plate 106 includes two inlets 134, 136 and two outlets 138, 140.
  • Inlet 134 is in fluid communication with two auxiliary intake ports 142, 144, while inlet 136 is in fluid communication with two auxiliary intake ports 146, 148.
  • outlet 138 is in fluid communication with two auxiliary discharge ports 150, 152, while outlet 140 is in fluid communication with two auxiliary discharge ports 154, 156.
  • auxiliary intake ports and auxiliary discharge ports 142-156 are located such that when the pressure plates 106, 108 are assembled to the rotor 102/cam ring 104 assembly, the rotation of the rotor 102 brings the auxiliary intake ports and auxiliary discharge ports 142-156 into fluid communication with each of the notched areas 118 on rotor 102.
  • the dual-lobe configuration of the cam ring 104 offers the potential for balancing rotor pressures during pump operation such that bearing loads are considerably reduced.
  • the pressure plate inlets 134, 136 are spaced 180° apart, and the outlets 138, 140 are also spaced 180 degrees apart, the pressures are balanced around the 360 degrees of the rotor.
  • the pressure-induced loads on the rotor 102, cam ring 104, and bearings may be very small.
  • This balanced pressure feature allows for the use of smaller, lighter bearings and drive shafts as compared to those typically used on pumps having single-lobe cam rings.
  • the dual-lobe cam ring design allows for two inlets and two outlets, the pump can provide the same output flow in a smaller package with a lower inlet pressure than the typical positive displacement pump with a single-lobe cam ring.
  • FIG. 5 illustrates a prior art rotor/cam ring assembly 160.
  • the rotation of rotor 162 causes the vanes 114 to alternately extend and retract as the vanes 114 move through pumping chambers 164, 166.
  • one vane constitutes the leading vane, the other the trailing vane.
  • the space between the leading vane and the trailing vane defines a volume. Fluid entering the pumping chambers 164, 166 via pressure plate inlets 168, 170 fills this volume and is discharged at outlets 172, 174.
  • the rotational velocity of rotor 162 generates such centrifugal force that the vanes 114 effectively seal against the inner diameter 122 (shown in FIG. 3 ) of cam ring 104.
  • the vanes 114 reach their maximum extension. After reaching maximum extension, the vanes 114 then begin retracting into slots 112 as they rotate through one of the pumping chambers 164, 166 toward the minor diameter 178 and through one of the discharge outlets 172, 174.
  • variable displacement feature allows the cam ring 104 to be rotated so that, for each intake and discharge cycle, less than the maximum amount of fluid may be drawn in from each of the inlets 168, 170 during the intake cycle, and similarly, less than the maximum is discharged into the each of the outlets 172, 174 during the discharge cycle.
  • an embodiment of the pressure plate is configured to address the problems of cavitation and pressure pulsation common to prior art dual-lobe variable displacement pumps.
  • Auxiliary intake ports 142, 144, 146, 148 are positioned near each of the two inlets 134, 136.
  • Two auxiliary intake ports 142, 144 are in fluid communication with inlet 134, while the two other auxiliary intake ports 146, 148 are in fluid communication with inlet 136.
  • auxiliary discharge ports 150, 152, 154, 156 are positioned near each of the two outlets 138, 140.
  • Auxiliary discharge ports 150, 152 are in fluid communication with outlet 138, while auxiliary discharge ports 154, 156 are in fluid communication with outlet 140.
  • FIG. 6 illustrates a rotor/cam ring assembly 180 according to an embodiment of the invention.
  • the cam ring 104 is rotated slightly relative to the pressure plate 106, to slightly decrease the maximum displacement, the cam ring lobes 124, 126 are positioned such that the vanes 114 will start to extend before reaching either of the inlets 134, 136.
  • the effects of rapid decompression in the volume between a pair of vanes 114 is reduced due to the auxiliary intake ports 142-148 being positioned to increase the available supply of fluid, via one of the notches 118 in the rotor 102, to one of the pumping chambers 182, 184 as required by the increased gain of the cam which results due to the turndown condition, or rotation of the cam ring 104.
  • auxiliary discharge ports 150-156 In the same manner, pressure pulsation is effectively avoided due to the positioning of auxiliary discharge ports 150-156 near outlets 138, 140.
  • the slight rotation of the cam ring 104 causes the rotating vanes 114 to start retracting before reaching either of the outlets 138, 140.
  • Pressure pulsation is reduced due to the auxiliary discharge ports 150-156 being positioned such that, as the vanes 114 retract, pressure on the fluid between the vanes is relieved when the fluid is forced through one of the auxiliary discharge ports 150-156 to one of the outlets 138, 140.
  • the discharge path provided by the auxiliary discharge ports 150-156, when the cam ring 104 is rotated away from maximum displacement, allows the pump to operate continuously without the damaging effects of pressure pulsation.
  • the lobes 124, 126 may be positioned relative to the pressure plates 106, 108 such that a pair of vanes 114 may be at, or near, maximum extension when the volume between those vanes 114 initially comes into fluid communication with one of the inlets 134, 136 and its associated auxiliary intake ports 142-148 via the rotor notches 118. It then follows that the pair of vanes 114 would also start retracting while still rotating through one of the inlet 134, 136 regions causing some fluid to flow back into one of the inlets 134, 136 and the associated auxiliary intake port 142-148 during the intake cycle, thus effectively reducing the pump displacement. In this manner, the variable displacement concept is realized because the intake flow is returned to the inlet without doing any significant amount of work on the fluid.
  • the rotation of the pair of vanes 114 takes the volume between those vanes 114 out of fluid communication with one of the inlets 134, 136 one of the associated auxiliary intake ports 142-148, the volume then comes into fluid communication with, and discharges fluid into, one of the outlets 138, 140 and one of the associated auxiliary discharge ports 150-156 via one of the rotor notches 118.
  • the pair of vanes 114 will have retracted substantially by the time the volume between the vanes 114 comes into fluid communication with one of the outlets 138, 140 and associated auxiliary discharge ports 150-156.
  • the fully retracted vanes 114 pass through one of the non-lobed regions 128, 130 to the other of the pumping chambers 164, 166.
  • the leading vane 114 starts to extend into the other of the two pumping chambers 164, 166, the volume between the pair of vanes is still in fluid communication with one of the outlets 138, 140 and one of the associated auxiliary discharge ports 150-156.
  • the pressure drop created by the expanding volume between the pair of vanes 114 causes some of the fluid from the outlet 138, 140 and from the associated auxiliary discharge port 150-156, via a rotor notch 118, to be pulled back into the pumping chamber 164, 166.
  • auxiliary intake ports and auxiliary discharge ports 142-156 serve to reduce both the pressure pulsation and the cavitation that can severely limit the usefulness of variable-displacement, dual-lobe, single-ring vane pumps.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Claims (12)

  1. Pompe (100), comprenant:
    une plaque de pression (106) comportant deux entrées (134, 136) et deux sorties (138, 140), et
    un ensemble d'anneau de came/rotor (102, 104) adjacent à la plaque de pression, l'ensemble d'anneau de came/rotor (102, 104) comprenant:
    un anneau de came rotatif (104) comportant une ouverture bilobée (122);
    un rotor (102) disposé à l'intérieur de l'ouverture bilobée (122) de l'anneau de came, le rotor (102) comportant une pluralité de fentes radiales (112) et présentant une pluralité de régions encochées (118) entre des fentes radiales adjacentes (112) ; et
    une pluralité d'aubes (114) configurées de manière à se déplacer à l'intérieur des fentes radiales (112);
    dans laquelle une chambre de pompage (182) est définie par un espace entre le rotor (102) et l'anneau de came (104);
    dans laquelle la rotation du rotor (102) à l'intérieur de l'anneau de came (104) entraîne la pluralité d'aubes (114) à s'étendre et à se rétracter radialement à l'intérieur de la chambre de pompage (182);
    caractérisée en ce que chaque entrée (134, 136) présente un port d'admission auxiliaire (142, 146) en communication fluidique avec l'entrée, et chaque sortie (138, 140) présente un port de décharge auxiliaire (150, 154) en communication fluidique avec la sortie, et
    dans laquelle le déplacement des aubes (114) et la rotation du rotor (102) sont configurés de manière à décharger dans les sorties (138, 140) et des ports de décharge auxiliaires (150, 154) un fluide aspiré dans la chambre de pompage (182) par l'intermédiaire des entrées (134, 136) et des ports d'admission auxiliaires (142, 146).
  2. Pompe selon la revendication 1, comprenant en outre un espaceur (110) qui comporte une ouverture centrale configurée de manière à maintenir l'anneau de came rotatif (104), dans laquelle l'espaceur (110) est attaché à la plaque de pression (106).
  3. Pompe selon la revendication 2, dans laquelle l'espaceur (110) permet à l'anneau de came rotatif (104) de tourner à l'intérieur d'une ouverture courbe de l'espaceur (110).
  4. Pompe selon la revendication 1, dans laquelle le rotor (102) est sensiblement circulaire, et dans laquelle l'ouverture de l'anneau de came (104) est un cercle à lobes.
  5. Pompe selon la revendication 4, dans laquelle les deux lobes (124, 126) de l'anneau de came sont espacés de 180 degrés l'un de l'autre.
  6. Pompe selon la revendication 1, dans laquelle les régions encochées (118) sont positionnées de manière à être en communication fluidique avec les ports d'admission auxiliaires (142, 146) et les ports de décharge auxiliaires (150, 154).
  7. Pompe selon la revendication 1, dans laquelle l'anneau de came (104) est configuré de manière à tourner dans une pluralité de positions par rapport à la plaque de pression (106).
  8. Pompe selon la revendication 7, dans laquelle la position de l'anneau de came (104) régule le volume de fluide aspiré dans la chambre de pompage (182) à partir des entrées (134, 136).
  9. Pompe selon la revendication 1, comprenant en outre:
    une seconde plaque de pression (108) comportant une première entrée et une première sortie;
    dans laquelle:
    l'anneau de came (104) comprend une poignée (132) configurée de manière à faire tourner la position de l'anneau de came (104), et
    le rotor est configuré de manière à tourner à l'intérieur de l'ouverture bilobée,
    la pluralité d'aubes sont disposées à l'intérieur des fentes de rotor,
    l'anneau de came (104) et le rotor (102) sont disposés entre la plaque de pression (106) et la seconde plaque de pression (108), et
    la rotation du rotor et le déplacement des aubes entraînent l'admission d'un fluide en provenance des entrées et la décharge du fluide vers les sorties.
  10. Pompe selon la revendication 9, comprenant en outre un espaceur comportant une ouverture centrale, dans laquelle l'espaceur (110) est positionné entre la plaque de pression (106) et la seconde plaque de pression (108).
  11. Pompe selon la revendication 10, dans laquelle la poignée (132) est configurée de manière à faire tourner l'anneau de came (104) à l'intérieur d'une ouverture courbe dans l'espaceur (110).
  12. Pompe selon la revendication 9, dans laquelle chacune des plaques de pression comporte deux entrées (134, 136) espacées de 180 degrés l'une de l'autre et deux sorties (138, 140) espacées de 180 degrés l'une de l'autre.
EP10808606.7A 2009-08-11 2010-08-10 Pompe à palettes équilibrée en pression, à déplacement variable, à deux lobes et une bague Active EP2464872B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US12/538,926 US8348645B2 (en) 2009-08-11 2009-08-11 Balanced pressure, variable displacement, dual lobe, single ring, vane pump
PCT/US2010/044960 WO2011019684A2 (fr) 2009-08-11 2010-08-10 Pompe à palettes équilibrée en pression, à déplacement variable, à deux lobes et une bague

Publications (3)

Publication Number Publication Date
EP2464872A2 EP2464872A2 (fr) 2012-06-20
EP2464872A4 EP2464872A4 (fr) 2016-06-08
EP2464872B1 true EP2464872B1 (fr) 2018-03-14

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EP10808606.7A Active EP2464872B1 (fr) 2009-08-11 2010-08-10 Pompe à palettes équilibrée en pression, à déplacement variable, à deux lobes et une bague

Country Status (5)

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US (1) US8348645B2 (fr)
EP (1) EP2464872B1 (fr)
CN (1) CN102498298B (fr)
CA (1) CA2770324C (fr)
WO (1) WO2011019684A2 (fr)

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JP6681705B2 (ja) 2015-12-16 2020-04-15 株式会社ショーワ ベーンポンプ装置
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CN107939677B (zh) * 2017-10-30 2019-07-23 兰州理工大学 一种液环泵
US10982757B2 (en) * 2018-07-17 2021-04-20 GM Global Technology Operations LLC Hydraulic control system for a continuously variable transmission
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Also Published As

Publication number Publication date
US8348645B2 (en) 2013-01-08
CA2770324C (fr) 2015-09-22
EP2464872A4 (fr) 2016-06-08
CN102498298A (zh) 2012-06-13
WO2011019684A2 (fr) 2011-02-17
CN102498298B (zh) 2015-04-01
EP2464872A2 (fr) 2012-06-20
CA2770324A1 (fr) 2011-02-17
US20110038745A1 (en) 2011-02-17
WO2011019684A3 (fr) 2011-05-26

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